Hydraulic device for the transmission of power



Aug- 8, 1939 D. sENsAUD DE LAvAuD 2,168,862

) HYDRAULIC DEVICE FOR THE TRANSMISSION OF POWER i? Filed Dec. 1o, 195s11 sheets-sheet 1 i767? '475 fe@ (/Wnr. A?, W37) z lNvENTOR.-DIMITRIENSAUDDE LAVAL/D1 fax/www@ d ATTORNEys Allg 8, l939- D. sENsAUDDE LAVAUD 2,168,862

HYDRAULIC DEVICE FOR THE TRANSMISSION OF POWER Filed Deo. lO, 1956 llSheets-Sheet 2 INVENTORz E SENSAUD DE LAVAUD Y m ATToRNEx/ g mmomw/ lg8, 1939. D. sENsAuD DE LAVAUD 2,168,862

HYDRAULIC DEVICE FOR THE TRANSMISSION OF POWER lOl Sheets-Sheet 3 FiledDec. l0, 1956 INVENTOR: DIMITRISENAUD DE LAVAUD f ,@CW ATTORNEYS Aug- 8,1939. D. sr-:NsAUD DE I AvAUD 2,168,862

HYDRAULIC DEVICE FOR THE TRANSMISSION 0F POWER Filed Deo. lO, 1956 11Sheets-Sheet 4 INVENTOR= DIMITRI SEMS/AUD DE LAVAUD BY @QC/ vg ATTORNEYSAl1g- 8, 1939 D. sENsAuD DE LAvAuD 2,168,862

HYDRAULIC DEVICE FOR THE TRANSMISSION OF POWER Filed Dec. l0, 1956 llSheets-Sheet 5 AVAUD O R OL m TE E @D D VUm WM m N E ,o WY IIB W D Aug-8, 1939 D. sENsAUD DE I AvAuD 2,168,862

HYDRAULIC DEVICE FOR THE TRANSMISSION OF POWER Filed Dec. lO, 1936 llSheets-Sheet 6 l N VENTO R: DI [Vl/TRI ENAUD DE LAVAUD BY 8kg ATTORNEYSD. sENsAUD DE LAVAUD' HYDRAULIC DEVICE FOR THE TRANSMI SS ION OF POWERFiled Dec. l0, 1936 ll Sheets-Sheet 7 wav ' INVENTQR: DJMITR: ENSAUD-DE,LAVAUD BY Kb@ ATTRNEY Aug- 8, 1939- D. sENsAUD DE L AvAuD 2,168,862

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HYDRAULIC DEVICE] FOR THE TRANSMISSION 0F POWER Filed Dec. l0, 19556 llSheetS-Sheet 9 INVEN'T'ORI DMTRI ENAUD DE LAVAUD 04! ATTORNEY Filed Dec.1o, 19:56 11 sheets-sheet 1o D M wm OL mm w mm N E foA mm n m D @W w /mD. SENSAUD DE LAVAUD Aug. s, 1939.

HYDRAULIC vDEVICE FOR THE TRANSMISSION 0F POWER lu 3, l939` D. sENsAUDDE LAVAUD 2,168,862

HYDRAULIC DEVICE FOR THE TRANSMISSION OIF POWER D n u@ n :Wn @u u RA OLH TE N ND ,R E D f O Y a VAUn u. NL/,A N ,4 E r 51, m4 I m.. m W w. w. D

Filed Dec Patented Aug. 8, 1939 HYDRAULIC DEVICE FOR THE TRANSMIS- SIONOF POWER l Dimitri Sensaud de Lavaud, Paris, France Application December10, 1936, Serial No. 115,087

v In France December 17, 1935 7 Claims. Cl. 60-54) The present inventionrelates to improvements in hydraulic devices for the transmission ofpower, in which, co-axially with a pump, rigidly secured on a drivingshaft, are arranged a turbine, rigidly secured on a driven shaftco-axial with the driving shaft, and a ring provided with guide bladesplaced between the outlet of the turbine blades and the inlet of thepump blades, said ring, co-aXial with the turbine and with the pump,being connected to the fixed frame of the device through the medium of amovement selecting device such that it prevents the rotation of saidring in reverse direction to the rotation of the pump and turbine, butthat it allows this rotationin the same direction as that of theseelements when the latter rotate at the same speed, that is to say whenthe device operates as a coupling.

The invention is mainly characterised by the fact that, in order toobtain an optimum `eiiil ciency whatever may be the gearing down ratio,that is to say whatever may be the speed ratio between the pump andturbine, the blades of the turbine have a rigid convex dorsal portionand a iiexible concave ventral portion, and the blades of the pumps haveat least a iiexible portion at their inlet ends.

The present invention also includes a number of particular points whichwill appear from the following description with reference to theaccompanying drawings, given 'by way of example only, in which:

Fig. 1 is a sectional elevation of a form of construction of an improvedhydraulic transmission device according to the invention.

Fig. 2 is a diagrammatic sectional view, on an enlarged scale, of thehydraulic circuit proper.

Fig. 3 is a cross section made according to lines 13a-3a, lib-3b, 3c-3,respectively of Fig. 2, from left to right of Fig. 3.

Fig. 4 is a cross section made according to lines lla-4a and 1lb-4brespectively of Fig. 1, showing more particularly the circuit ofA theiiuid through the gear pump.

Fig. 5 is a partial cross section made according to line 5-5 of Fig. 1,showing the movement selecting device.

Fig. 6 is a diagrammatic sectional view of a constructional modificationof a blade of the '0 pump.

Fig. 7 is a diagrammatic sectional view of the vanes of the turbine andof those of the pump upon starting of the turbine and for a'speed zeroof the latter.

Fig. 8 is a diagrammatic View similar to that of Fig. 7 for a speed ofrotation of the turbine equal to about one half that of the pump.

Fig. 9 is a diagrammatic View similar to Figs. 7 and 8, but for a speedof rotation oi the turbine substantially equal to 3A. of that of thepump.

Fig. 10 is an axial sectional elevation of a second form of constructionof an improved hydraulic transmission device according to the invention.

Fig. 11 is a diagrammatic view, on an enlarged scale and in crosssection, of the hydraulic circuit proper, according to Fig. 10.

Fig. 12 is a section made respectively along line I 2a of Figs. 10 and11 in the left-hand portion of this figure, and along line l2b ofv Figs.10 and 11 in its right-hand portion, showing respectively the blades ofthe pump and those of the turbine.

Fig. 13 is a partial section made according to line XIII- XIII of Fig.11, showing the hydraulic connection device between the shell of theturbine of the ring of magnetic metal mounted on the latter and forminga part of the electromagnetic coupling device.

Fig. 14 is a detail cross section made according to line X[V-XIV of Fig.10, showing a form of construction of a pressure pump with inner gears.

Fig. 15 is a diagrammatic sectional view of the vanes of the turbine andof those of the pump upon starting of the turbine and for a speed zeroofthe latter.

Fig. 16 is a diagrammatic view similar to that oi Fig. 15 for a speed ofrotation of the turbine equal to about one half that of the pump.

Fig. 17 is a diagrammatic view similar to Figs. 15 and 16, but for aspeed of rotation of the turbine approximating that of the pump.

Fig. 18 is a front view of the device automatically controlling thedeformation of the ventral parts of the turbine blades, this devicebeing shown in lateral elevation in Fig. 11.

In the various iigures of the drawings, the s ame reference numbers orcharacters designate the same parts or parts fulfilling the samefunction.

On a driving shaft l is secured, by bolts 3, the shell 2e of a pump, theother shell 2b of which is connected to the shell 2a by any suitablemeans. Thus, in the example illustrated, both shells are rendered rigidtogether by means of screws 4 arranged in flanges provided on theperiphery of shells 2a and 2b. Fluid-tightness between these two shellsis ensured in any suitable manner and for instance by a ring 5, having acircular cross section, made of a relatively plastic or malleablematerial and fitting into grooves of corresponding shape provided in theopposite faces of shells 2a and 2b.

On the shell 2b of the pump are secured blades which, according t-o theinvention, are flexible at least on the side the uid enters the pump.For that purpose, each blade of the pump is constituted, in the firstplace, by a rigid part I I located at the place where the fluid issuesfrom the pump and which is secured, by any suitable means, on the onehand, on the shell 2b, or on av cheek member. 9 rigid with this shell 2band, on the other hand, on a circular inner crown or ring I (see Figs. 2and 3). Each of these rigid parts II is preferably arranged in a planepassing through the axis of rotation common to the turbine and to thepump. In the second place, eachblade of the pump 2 is constituted, onthe side the fluid enters-said pump, by a flexible vane 6. Y

At the end Aof this vane 6, located on the side the fluid enters pump 2,the edge of said vane 6 is bent down at 'I for forming a socket in whichfits a rod 8 the .ends of which are secured, on the one hand,'in theshell 2b or in the circular cheek member 9 rendered rigid with this'shell 2b and, on the other hand, in the circular inner crown or ring IU.It will therefore be seen that said vane 6 can pivot about rod 8 at thesame time as it becomes distorted under the action of. the thrustexerted by the uid. In order to limit this pivotal movement, each of thevanes 6 has such a length that it abuts, at its free edge, on the tworigid parts II* adjacent to the vane 6 under consideration and locatedon vthe side the uid issues from pump 2. The position of the'rod 8,relatively to these two rigid parts II is determined in any suitablemanner and it is for instance located, as illustrated, midway of thedistance separating these two rigid parts II, but it is obvious thatthis rod 8 might be placed in any other intermediate position forobtaining a suitable distortion of said flexible vane 6 for a definitethrust of the fluid.

According to the invention, Itwl'iewpiulurrip blades can also beconstituted by vanes flexiblejt; frgl'E (outth'eir length withoututilizin/g/iixedwhladl pp gagsjagspnvmrijrh this Case, the blades wouldbe secured, on the one hand, by the rods 8 and, on the other hand, by'rods secured on said vanesat'an intermediate point of their length, butpreferably situated nearer the outlet edge than to the edge where thefluid enters, these rods being guided in diametral planes on the shell2b of the pump, or on the cheek member 9 and on the inner circular crownor ring III, so as to allow bending of said Vanes under the action ofthe thrust exerted by the fluid.

The blades of the pump 2 might also be constituted by rigid vanessubstantially arranged in diametral planes.

On the crown I0 is secured, by screws I3 for instance, a ring I4, madeof magnetic material, which serves as fixed armature for the winding Iof an electromagnet, the function of which will be explained later on.One of the ends of this winding is earthed or grounded, whilst its otherend is connected to a terminal IE secured on the shell 2b of the pump inany suitable manner, but electrically insulated therefrom. This terminalI 6 is electrically connected, by a wire I'! or the like, insulated fromthe shell 2b, to a collector ring I8 rendered rigid with said shell 2bby rivets I9 or the like, but electrically insulated therefrom. r

A brush 2U wipes against this ring I8, and this brush 20 is secured onthe fixed casing 2I of the device by any suitable means. At its end,this brush 20 is provided with a suitable current supply device.

At the end of a shaft 22, which can be either the driven shaft itself,or be connected tothe latter by a gear relay or the like, is rigidlysecured the hub 23 of the shell 24 of the turbine of the hydraulicdevice. This hub 23 is rotatably mounted on the driving shaft I or onthe shell 2-a of the pump which is rendered rigid therewith by means ofa ball bearing 25, or the like carried by the driving shaft I. On theshell 24 of the turbine, blades 26 are secured as will now be described.Each of these blades 26 is constituted by two elements 26a and 26b lyingadjacent at their inlet ends. The element 2tn of each blade, whichconstitutes the dorsal face of the latter, is rigidly secured at bothits ends and by any suitable means, on the one hand, on the turbineshell 21, and, on the other hand, on an inner cheek member 21 which isthus rendered rigid with the turbine shell 24. In a convenient form ofconstruction, the element 2Gb of the blade is provided, at both itsends, with two small side projections fitting into suitable perforationsformedin the shell 24 and cheek member 21, and which aresubsequentlybent down or riveted on the outer sidesV of this shell 24and cheek member 2T.

The element 2Gb of the blade is rigid, whilst the ventral portion 26a isresilient. siliency of this ventral part 26a is such that it tends tomove the outlet edge of this part 2lia in contact with the dorsalelement 26b of the blade located behind it in the direction of therotation, so as to reduce the section of the passageway for the fluidbetween two adjacent blades but without completely blocking saidpassageway.

Between the ventral part 26a and dorsal part 2Sb of each of the bladesis arranged a finger 28, or the like, which is normally in contact withthe ventral part 2lia of the blade when the hydraulic device operates.The various fingers 28 are secured on a ring 29 angularly movablerelatively to the cheek member 21 and, consequently, relatively to theturbine shell 24. The relative angular displacement of this ring 29 isautomatically produced in function of the speed of rotation of theturbine by any suitable means, in such a manner that an increase ofspeed of the turbine produces a rotation of the ring 29 carrying thelingers 28 in such a direction that these fingers 28 act on the ventralelement 26a for pushing it back so as to reduce the section of thepassageway for the fluid between two adjacent blades; in other words,these lingers 28 act in the same direction as the resiliency of theelements 26a of the blades when the speed of the turbine increases.

An example of construction of a device for automatically controlling therotation of ring 29 will now be described. On the crown 21 and at twodiametrally opposed points are secured two.,

studs 39 on each of which is pivoted a centrifugal member 3l havingsubstantially the shape of a semi-circular ring.I The free end of thiscentrifuga-l member 3I is rendered rigid with a pin 32 secured on themovable ring 29, said pin 32 passing through a suitable aperture 33provided in the crown 2 and which is concentric with the pivot pin 3l)`of the corresponding centrifugal member 3|.

Likewise, and` in order to allow the rocking 30 of this centrifugalmember 3I.

movement of centrifugal member 3|, the pin 32 passes through an aperture34 of the centrifugal member and this aperture is extended according toa radius passing through the pivot pin The operation will be easilyunderstood. As soon as the speed of the turbine increases, centrifugalforce tends to cause the centrifugal members 3I to rock, the pins 32 aremoved in the direction of the arrow 35 and cause the ring 29 to rotatein the direction of this arrow 35. The centrifugal members 3l can berestored in the centripetal direction by any suitable means, such assprings, but the springs can be omitted, and alone the action'of the uidon the elements 26a of the turbine blades'can be utilised for restoringthe centrifugal members 3|, as will be 'explained later on.

A circular ring 36, made of magnetic metal,

is secured on the cheek member 21 of the turbine by any suitable means.This ring 36 is located opposite the ring' I4 serving as armature. forthe electromagnet I5 rigid with the shell 2b of pump 2. It will beeasily understood that the energization of electromagnet I5 causes thering 36 to be attracted, and the turbine 24 and pump 2 are then renderedrigid together. The circuit of electromagnet I5 can be closed manually.

The rings 36 and I4 and theinner peripheral shape of shells .221, 2b and24 are such that, at

the outlet of the pump blades is formed wampassage 31 without blades andconstituting an en larged channel or diiu'ser for the fluid flowing fromthe pump outlet to the turbine inlet. For

that purpose, the variations inthe section of the passage 31 betweenthese two places willcorrespond to those usually admittedfor a diiuser.

In other words, the passage 31'will have a divergency between the pumpoutlet and the tur- 40 -lbine inlet substantially corresponding to thatof a diffuser having rectilinear sides forming together an angle ofabout 7. Such a diffuser considerably improves the operation of thehydraulic device and constitutes a very important feature of the presentinvention.

Avring 38, provided with blades 39, is concentric with the axis ofrotation common lto the turbine 24 and pump 2.

These blades 39 form inlet and outlet angles which are substantiallyequal; moreover, their inlet edge and their outlet edge aresubstantially situated at the same distance from the axis of rotationcommon to the turbine and pump.

Likewise, the flexible v'anes 6 forming a part vof the blades of pump 2have their inlet edges substantially situated at the same distance fromthe axis of rotation as the outlet edges of the blades 26 of turbine 24,and the inlet edges of the blades 26 of this turbine 24 are alsosituated substantially at the same distance from the axis of rotation ofthe various elements of the hydraulic device as the outlet edges of thexed portions I I of the pump blades.

The bladesjS are fixed and serve to directwand 70 the medium of a ballbearing 48, or the like, on

the hub 23 of the turbine shell 24. On the other hand, on pins 4I, ttedon the shell 38 of the guide vane or ring, are pivoted pawls 42 normallycoming in engagement with the teeth of a ratchet 75 43 rigidly securedon the end of a sleeve 44, the

other end of which is secured, by screws 45 for instance, on a member 46rigid with the xed frame 2I of the device. The pawls 42 are so arrangedas to prevent the rotation of the guide vanering 38 in reverse directionto that of turbine 24 and pump 2. These pawls 42 are balanced in orderto release at a certain predetermined speed, so that, when the pump 2and turbine 24 rotate at the same speed either owing to the hydrauliclocking, or owing to the operation of the electromagnetic devicerendering the turbine and pump rigid together, the guide vane ring 38can be driven in the same direction and at the same speed as thesetwoapparatuswithout the pawls A42 remaining. in contact withy the fteeth'ofratchet 43.,- Y.

I nv order to -avoid cavitations within. the hy- `draulic'circuit and tocompensate forfthe unconstitutedby two pinions 41 and`48 meshingtogether and arranged .within a -suitablecasing constituted, on'the onehand, by the member 46 and, on the other hand, by a member 6I on whichis attached the securing ange 62 of the xed sleeve 44. 3' l The pinion48 is, loosely mounted on a stud 49 secured to the casing of said gearpump, whilst pinion 41 is rendered angularly rigid, with a sleeve 59,concentric with sleeve v44 and thev other end of which is renderedrotatable with a ring 5I secured, by screws 52 for instance, on the pumpshell 2b. The suction of .this pump exerts itself through a piping 53,the free end of which l opens in a casing 54 constituted by the fixeframe 2I of the transmission device. l

According to the invention, the delivery of said gear pump passes fromthe'chamber 55 which connects to a conduit 56 connected to a piping 58.This piping 58 yis connected to a suitable radiator 10, or the like, theoutlet of which is connected to a piping 59. This piping 59 is connectedto a conduit 69 provided in the member 6I rigid with the frame 2I of thedevice and serving as casing for the pump. This conduit 6l] opens in anannular chamber 63, communicating with the annular space 64 providedbetween sockets 44 and 50, which space communicates in its turn with theinterior of the hydraulic device. The fluid leaves the converter throughthe bearing 25, the axial boring of the shaft 22 and, through radialholes of the latter, it returns to the casing 54.

It will therefore be seen that, by means of this arrangement, the fluid,delivered by the gear pump I1-48, passes into a radiator 10, or thelike, before entering the hydraulic device proper. It will therefore bepossible to cool the iluid to any desired temperature when this fluidtends to heat up, as this is particularly the case when the hydraulic.device operates during a very long time with a gearing down ratio. It isobvious that lters or the like can be arranged on the path followed bythe fluid.

Suitable fluid-tight packings 51 are provided at the various placeswhere the pressure of the iiuid is exerted, and in particular betweenthe casing or frame of the device and the interior of the hydrauliccircuit proper.

The operation of the improved hydraulic device according to theinvention will now be described in greater detail, particularlyconcerning the fluid circuit proper when the device operates withhydraulic gearing down ratio, that is to say, when the turbine rotatesless rapidly than the pump. It is known, in this case, that for eachratio between the speeds of rotation of the turbine andpump, it isindispensable, for obtaining satisfactory efficiency, that the variousinlet and outlet angles of the turbine blades and at least the inletangle of the pump blades should automatically vary in function of therelative speeds between the pump and turbine.

For greater clearness, the operation of the device will be describedfrom the starting of the turbine. Reference will be made for thatpurpose to Fig. '7 of the drawings. -Owing to the rotation of pump 2,the fluid is rotatively driven as a real body about the axis of rotationof the various elements of the device and in the direction of the arrowf. This fluid flywheel encounters the blades 26 of turbine 24, whichblades are fixed since said turbine is stationary. .The fluid thenenters the blades of this turbine according to the direction V2 and at aspeed V2. This fluid acts on the ventral element 26a of the blades forpushing it back, in antagonism to its resiliency, and moving it to theposition shown in full lines in Fig, 7. Owing to the fact that turbine24 does not yet rotate, the fluid issues with a speed V3 which issubstantially equal to V2, assuming the section of the passagewayremains constant throughout the path followed by the fluid in the blades26, the friction not being taken into consideration. The applicant hasfound that, in practice. it was convenient to slightly increase thespeed V3 of issue of the fluid by slightly reducing the section of thepassageway.

Turbine 24 being assumed stationary, the fluid enters the blades 39 ofthe guide vane ring 38 according to a speed V4 equal to and of the samedirection as V3. This fluid issues from the guide vane ring 38 at aspeed V5 substantially equal to V4, the losses by friction-not beingtaken into consideration and assuming the section of the passageway isthe same at the inlet and at the outlet of said guide crown 38 and thatthe inlet and outlet angles of the blades of the latter are equal.

The fluid enters the pump 2 according to a direction Wn which is therelative speed of admission of the fluid and which is the component ofthe absolute speed Vo of admission of the fluid equal to Vs with thetangential speed U0 of the pump. The fluid having this speed Wo acts onthe flexible vanes 6 forming a part of the pump blades and curves o1'bends them as shown in Fig. 7 in antagonism to their resiliency.

The fluid issues from the pump blades through the llxed parts Ilaccording to an absolute speed Wi which is substantially radial andcombines with the tangential speed U1 of pump 2 for giving a relativespeed V1 of issue of the fluid which is to be found once again at theoutlet of the diffuser 3l provided in pump 2.

The fluid to which the speed V1 is imparted acts on the blades of theturbine and tends to cause the latter to rotate in the direction ofarrow f. 'I'he turbine therefore rotates in the same direction as thepump.

The operation of the device will now be considered when the turbinerotates at a certain speed which has been chosen, in the present case,equal to half that of the pump (Fig. 8). The various speed vectors aredesignated by the same references as in Fig. 7, but with the indexprime.

The absolute speed of admission of the fluid V'z into the turbinecombines with the tangential speed Uz for giving a relative speed ofadmission of the fluid Wz into this turbine. This speed Wz is smallerthan the speed Vz (Fig. '7) so that the ventral portion 26a of theturbine blades curves in the direction of the-arrow J" under theinfluence of its resiliency and of the action of the centrifugal members3|. The section of the passageway for the fluid diminishes towards theoutlet of the turbine bladesv and the speed of flow of the liquidincreases from the inlet to the outlet of the turbine blades. Therelative speed with which the fluid Ws issues from the turbine combineswith the tangential speed Ua for giving the absolute speed of issue toV3 of the fluid which is equal to the speed of admission V'4 of thefluid into the recuperator.

The fluid issues from the guide vane ring 38 provided with the guideblades 39 at a speed V5 equal, the frictions being neglected, to thespeed V4. This speed V'5 combines with the tangential speed Uo of thepump for giving the relative speed of admission Wo into the pump. In theexample chosen, this speed Wo is radially directed so that the flexibleparts 6 of the pump blades are also radially directed for this value ofthe gearing down ratio between the pump and the turbine. It will be veryeasily understood that it is possible, by a judicious choice of theinlet angles of the turbine and guide vane ring and of the distancesseparating the inlet and the outlet of the pump blades and turbineblades, to obtain this radial direction of the flexible parts 6 of thepump blades for any desired value of the gearing down ratio betwen thepump and the turbine.

When the speed of the turbine exceeds, for one and the same speed of thepump, the value corresponding to that of the diagram of Fig. 8,reference will be made to the diagram of Fig. 9 in which the variousspeed vectors are designated by the same references as in Figs. '7 and8, but with the index "second. It will be seen that the speed. ofcirculation or relative speed of admission W"z of the fluid into theturbine further diminishes; the thrust of the fluid on the element 26nof the turbine blades therefore diminishes so that, under the influenceof their resiliency and of the fingers 28 moved by the centrifugalmembers 3l, said element 26a still further reduces the section of thepassageway for the fluid at the outlet of the turbine blades.

It will also be seen that the absolute speed V"0 of the fluid at theinlet of the pump blades combines with the tangential speed U"0 forgiving a relative speed W"o of admission of the fluid or speed of flowwhich will tend to curve the flexible portion 6 of the pump blades asshown in Fig. 9, that is to say in reverse direction to the curvaturethat this flexible portion 6 had upon starting of the turbine (Fig. '7)

When the turbine and the pump rotate at the same speed, owing to thesetting in action of the coupling device provide between the turbine andthe pump, there is no longer any relative sliding movement between thesetwo elements, the absolute speed of admission V2 into the turbine isnull, there is therefore no longer any circulation of fluid within thehydraulic circuit. From this fact, W2 is null and the ventral element26u of the turbine blades ts, by its outlet edge, on to the dorsalelement 2lib of the adjacent blade, thus completely obturating thepassage of the fluid in the turbine. The guide vane ring is thenrotatively driven in the same direction as the turbine and piunp, owingto the fact that the speed V4 is null and cannot therefore act forcausing said guide vane ring to be held stationary.

The fact of forming the turbine blades 28 of two elements 2lia and 2Gb,the ventral element 26a of which is resilient', so as to move towards'the dorsal element 2Gb of the adjacent blade and thus throttle thepassageway for the fluid, has moreover` an important advantage. In fact,it will be understood that, owing to the peculiar resiliency of theelement 25a, the fluid will be able to push back this element 26a onlywhen its speed of circulation will reach a certain value. Upon starting,this speed of circulation of the fluid in the turbine is equal to V1,that is to say is function of the speed of rotation of the pump. It willtherefore be understood that, for a speed of rotation of the pump lowerthan a certain value, the turbine will not be rotatively driven; thisprevents in particular the use of devices for braking or checkingthe-rotation of this turbine when ,a mechanical reversing device is usedand allows reference to Figs. 1 to 9, except concerning in particularthe constitution of the pump blades, the arrangement of theelectromagnetic members provided between the shells of the pump andturbine and rendering these latter rigid together, and thedevice-controlled by centrifugal force and causing the distortion of theresilient vanes constituting the ventral portion of the turbine blades.Therefore, these new elements alone will be described. In Figures 10 to18 the parts identical to those in Figure 1 are given the same referencenumerals.

On the shell 2b of the pump are secured blades which, in this form ofconstruction are constituted as follows: On the fluid outlet side of thepump are arranged a number of regularly spaced blades 88 constituted byat least one resilient vane the portion of which nearest the axis ofrotation of the device is secured, by any suitable means, on the onehand, on the shell 2h and, on the other hand, on an inner circular crownl0 (see Figs. 10 and 11) so as to be rigid on a certain height directedsubstantially according to a diametral plane.

In a form of construction which for the moment appears to beadvantageous, each blade 80 is constituted by a number of resilientvanes of diiferent lengths connected together by any suitable means andsecured on the shell 2b and on the crown by means of side projections 8|tting into suitable housings formed in the shell 2b and crown I0,respectively. Such a construction allows of obtaining a blade 80, theresiliency of which varies from the rigid portion used for securing theblade, to the free or outlet end of said blade.

On the other hand, on the side where the fluid enters the pump areprovided a number of ilexible blades 6, the number of which is equal tothat of Ithe blades 80 and each constituted by a resilient vane. At theend of this vane 6, located on the side the fluid enters the pump 2, theedge of said vane 6 is bent down at 1 for forming a socket in which ts arod 8 the ends of which are secured, on the one hand, in the shell 2band, on the other hand, in the inner circular crown l0.

It will therefore be seen that said vane 6 can pivot about the rod 8 atthe same time as it becomes distorted under the action of the thrust ofthe fluid. In order to linut this pivotal movement, each of the vanes 6has such a length that -midway of the distance separating these twoblades 8), but it is obvious that this rod 8 might be placed in anyother intermediate position for obtaining a suitable distortion of saidflexible vane 8 for a definite thrust of the fluid. l

It will be seen that, by means of such an arrangement, it is possible toobtain, for a given thrust of the fluid, a blade having a suitablecurvature, as shown in Figs. 12, 16 and 17 of the drawings.

On the shell 2a of the pump is provided a crown or ring I4', made ofmagnetic material, which serves as fixed armature for the winding 15 ofan electromagnet the function of which'will be explained later on. Oneof the ends of thiswnding I5 is earthed, whilst its other end isconnected, by a wire to a collecting ring |8 secured on the shell 2a ofthe pump in any suitable manner, but which is electrically insulatedtherefrom.

A brush or the like 28 resiliently wipes on this ring I8', and saidbrush 20' is secured on the fixed casing 2| of the device by anysuitable means. At its end, this brush 2U is provided with a suitablecurrent supply connection.

At. the end of a shaft 22, which can be either the driven shaft itself,or be connected to the latter by a gear or like relay, as will beexplained later on, is rigidly secured the hub 23 of the shell 24 of theturbine of the hydraulic device. This hub 23 is centered on the drivingshaft or on the shell 2a of the pump which is rendered rigid therewithby any suitable means. On the shell 24 of the turbine are secured blades26, in a similar manner to that described with reference to the rst formof construction illustrated in` Figs. 1 to 9.

In this second form of construction, the device automaticallycontrolling the rotation of the ring 29 is constructed as follows:

On the crown 2`| is secured a stud or pin 30 on which is pivoted aneccentric centrifugal member 3| on which a pivot pin 83 is secured. Onthis pivot pin 83 is also pivoted a centrifugal member 84 having a shapesimilar to that of the centrifugal member 3| and the other end of whichis journalled about a pivot pin 32 secured on the movable ring 29. Theoperation will be easily understood. As soon as the speed of the turbineincreases, centrifugal force tends to cause the centrifugal members 3|and 84 to pivot, the pivot pin 32 is driven in the direction of thearrow 35 and causes the rotation of ring 29 in the direction of thisarrow 35. The centrifugal members 3| and 84 can be restored in positionin the centripetal direction by any suitable means, such as springs, butthese springs can be omitted, and alone the action of the fluid exertedon the elements 2lia of the turbine blades, as will be ex-f plainedlater on, can be relied upon for restoring these centrifugal members 3|and 84 in position. A plurality of devices similar to that describedabove can be provided.

On the shell 24 of the turbine is secured, by any suitable means, acircular ring 36, made of magnetic metal. This ring 36 is locatedopposite the ring I4 serving as armature for the electromagnet I5 rigidwith the shell 2b of pump 2.

The operation of this electromagnetic device is the same as thatdescribed with reference to Fig. 1 of the drawings.

In this form of construction and in order to avoid the shells of thepump and turbine being suddenly rendered rigid together when theelectromagnet I5 is energized, instead of rigidly securing the ring 36on the shell 24 of the turbine, this ring 36 can be connected to theshell 24 by means of resilient, hydraulic or like devices. In a form ofconstruction which for the moment appears to be advantageous, the ring36 is provided with a number of radial grooves or flutes 85 in each ofwhich fits a radial rigid blade 86 (Fig. 13).

The various blades 86 move in a circular enclosure 81 bound, on the onehand, by the shell 24 of the turbine, and, on the other hand, by a crownor ring 88 to which the blades 86 are secured by any suitable means.Fluid-tightness between said crown or ring 88 and the shell 24 of theturbine is ensured by the fact that, in its inner portion, this crown 88ts between the side face of said shell 24 and a cheek member 89 securedon said shell 24 by any suitable means, such as rivets 90.

A number of radial blades 9| rigid with the shell 24 of the turbine areprovided within said circular enclosure 81 between the radial blades 86,The whole is filled with liquid or other suitable fluid, preferablyunder pressure, and in a convenient embodiment, the fluid iilling theenclosure is the same and is under the same pressure as that filling thehydraulic circuit. When the winding i5 is not energized, the ring 36rotates freely into the shell 24 of the turbine without contact betweenthe blades 86 and 9|. But, when the winding |5' is energized, the ring36 is immediately applied upon the crown I4 of the pumps and the liquidbetween the blades 9| and 86 is laminated and creates a damping effect Aavoiding a prejudicious shock between the blades 86 and 9|.

Concentric with the axis of rotation common to the turbine 24 and pump2, is arranged a ring 38 provided with blades 39 and which is similar tothat described in the first form of construction with reference to Figs.1 to 9 of the drawings. The arrangement of the inlet and outlet edges ofthe various blades of the pump, turbine and of the guide blades 39 issimilar to the arrangement shown in the form of construction of Figs. 1to 9. Likewise, the shell 38 carrying the guide blades is mounted in amanner similar to that shown in Fig. 5 of the drawings.

In order to avoid cavitations within the hydraulic circuit and forcompensating the unavoidable leakage of liquid, the uid is put underpressure within the hydraulic device by means of a gear pump forinstance. In this second form of construction illustrated in particular.in Figs. 10 and 14, this pump is constituted by an internally toothedring gear 92 and a pinion 41 gearing together and housed within a casingsuitably composed, on the one hand, of a member 46 and, on the otherhand, of a securing ange 62 of the xed sleeve 44.

The toothed ring gear 92 is loosely mounted, whilst the pinion 41 isrendered angularly rigid, by a clutch for instance, with a socket 50,concentric with the socket 44 and the other end of which is rigid withthe shell 2b of the pump. The suction of this pump takes place through apiping 53, the free end of which opens in a perforation 54 provided inthe xed frame 2| of the transmission device and communicating with thesuction chamber proper 93 of the pump.

The delivery of said 'gear pump takes place in a chamber 55 in whichopens a conduit 56 which opens, on the other hand, in an annular recess94. This annular chamber 94 communicates with the annular space 64provided between the sockets 44 and 50, which annular space 64communicates in its turn with the interior of the hydraulic device. Theluid leaves the converted through conduits 51a, enters the axial boringof the shaft 22 and returns to casing 2| through suitable radial holesprovided in the said shaft 22.

The shell 38 of the ring carrying the guide blades 39 is laterallycentered by suitable abutments 95, such as Mitchell abutments, betweenthe shell 2b of the pump and the shell 24 of the turbine.

Suitable fluid-tight packings 51 are provided at the various placeswhere the pressure of the fluid is exerted, and in particular betweenthe casing or frame 2| of the device and the interior of the hydrauliccircuit proper.

Concerning the operation of the second form of construction of thehydraulic device described with reference to Figs. 10 to 1'1, thisoperation is similar to that described for the rst form of constructionwith reference to Figs. 7, 8 and 9 and will not be described here ingreater detail.

The same reference numbers or characters designate the same parts or thesame speed vectors in Figs. 15, 16 and 17 as in Figs. 7, 8 and 9 whichsubstantially correspond thereto. One of the essential differencesresides in that, owing to the fact that the rigid portion of the pumpblades is replaced by a ilexible portion 80, the absolute outlet speedW1 of the iluid of the pump, instead of being always directed radially,is in the case of Fig. 15, rearwardly inclined relatively to thedirection of rotation of said pump and, in the case of Fig. 17, it isforwardly inclined relatively to this direction of rotation.

In order to facilitate the cooling of the fluid contained within thehydraulic circuit, the shell 2b of the pump can be externally providedwith a number of blades |26 acting as a fan and adapted to acceleratethe circulation of air along the shell 2b, suitable openings |21 beingprovided in the casing 2|.

The present invention also relates to a reversing device provided withgears constantly in engagement and constituted as follows: On one of theends of the shaft 22, on the other end of which is rigidly secured thehub 23 of the shell 24 of the turbine, is provided a bevel sun wheel 96.This bevel sun wheel 96 meshes with a number of bevel planet pinions 91journalled about radial pins 98 secured on a drum 99 provided at the endof a socket |00. A cheek member secured on the end of drum 99 by bolts|02, serves as side abutment for the bevel sun wheel 96. The bevelplanet pinions 91 mesh, on the other hand, with a bevel sun wheel |03provided at the end of the driven shaft proper |04. On the other .end ofthis driven shaft |04 is rigidly secured a coupling plate |05 or thelike. This shaft |04 is journalled in the frame 2| of the device throughthe medium of a ball or like bearing 0 6.

The periphery of the socket |09 is fluted and a sleeve |01, havingcorresponding lflutes. is

mounted on said socket so as to be ngularly rigid therewith, but so asto be capable of axially moving relatively `to said sleeve by anysuitable means. For that purpose, the sleeve |01 is provided with agroove or the like |08 in which llt the two arms of a fork-member |09guided parallel to the axis of shaft |04 by means of a rod or lthe likeI I rigid therewith and which is itself guided in corresponding bearingsprovided on the frame 2|. At its upper part, this forkmember |09 has ahousing I I2 into which flts the end ||4 of a lever III:` having aspherical portion the casing or frame 2|.

On shaft |04 is keyed a socket provided on its periphery with teeth ||9,corresponding to the flutes formed on the periphery of socket- |00, andwith which can engage the inner flutes of the sleeve |01 when the latteris moved in the direction of the arrow |20 by means of lever I6, so asto render said sleeve |01 angularly rigid with the shaft |04, for thepurpose which will be explained later on.

At the opposite end of socket I I8, the sleeve |01 is provided withouter teeth |2| which can engage, when the sleeve I 01 is moved, in adirection reverse to that indicated by the arrow |20, by means of thelever I6, with corresponding inner teeth |22 provided on a crown |23rendered rigid, by any suitable means such as screws |24, with the frameor casing 2| of the device. A ball |20, pushed back by a spring |29 canenter housings |30, |3| vand |32 respectively corresponding to the threepositions above defined and formed in the rod ||0..

4The operation of this reversing gear 'is as follows:

When the sleeve |01 is in its central position shown in Fig. of thedrawings,l it will be seen that the socket |00, comprising the drum 99with `which are rigidthe pins 98 of planet pinions 91,

can loosely rotate, so that the driven shaft |04 remains stationary when-the intermediate shaft 22 is rotatively driven. This is the rest ordead center position.

When the user moves lever I I 6 in the direction of' the arrow |25, hecauses the displacement of sleeve |01 in the direction of the arrow |20,so' that this sleeve |01, and consequently the socket |00, are renderedangularly rigid'with the socket II8 and therefore with the driven shaftA|04. It will then be seen that the intermediate shaft 22 isrenderedrigid with the driven shaft |04.

This is the direct drive position.

If, on the contrary, the user moves, from the dead center position, thelever ||6 in a direction reverse to that indicated by the arrow |25, hecauses the displacement of the sleeve |01 in a direction reverse to thatindicated by the arrow |20, so that this lsleeve |01 and consequentlythe socket |00 are rendered angularly rigid with the ilxed crown I 23and from this fact are held stationary. It' will then be seen that theintermediate shaft 22 and the driven shaft |04 rotate in reversedirection and at the same speed. This is the so-called reverse driveposition.

Owing to this arrangement and to the fact that the bevel sun wheels 96and |03 are identical, it will be seen that it will be possible toobtain efficient braking of the driven shaft |04 when this is required.Thus, in particular, when the power transmission hydraulic devicedescribed above in usedon a motor vehicle, it will be possible, owing tothis reversing gear having a gear ratio of-1/1 in reverse drive, toobtain efficient braking of the vehicle by mans of the engine when thisvehicle goes downhill, In fact, the user will move lever ||6 to thereverse drive position, and this will have the effect of driving 'shaft22, on which -the turbine 24 is keyed, in reverse' direction to that ofdriving shaft on which the pump 2 is keyed. A stirring of the fluidwithin the hydraulic circuit will thus be obtained and this will havefor effect to brake the driving shaft or, in other words, efficientbraking of the driven shaft |04 will thus be obtained through the mediumof the engine.

The present invention is not limited to the forms of constructiondescribed above and illustrated, but it extends to all those utilisingthe features above set forth and allowing to obtain the desired result.

What I c laim as my invention and desire to secure by Letters Patent is:

1. In an hydraulic transmission, a stationary casing, a driving shaft, arotary pump secured to said driving shaft and provided with bladeshaving at least a flexible portion at their inlet ends, a driven shaftcoaxial .with said driving shaft, a rotary turbine secured to saiddriven shaft and provided with blades having a rigid convex dorsalportion and a flexible concave ventral portion, a

guide vane ring in thereturn circuit between said turbine and said pump,a ratchet mechanism to lock the guide wheel to the casing when the pumpand the turbine rotate at different speeds.

2.In an hydraulic transmission, a stationary casing, a driving shaft, arotary pump secured to said driving shaft and provided with bladeshaving at least a flexible portion at their inlet ends, a driven shaftcoaxial with said driving shaft, a rotary turbine secured to said drivenshaft and provided with blades having a rigid convex dorsal portion anda flexible concave ventral portion, a guide vane ring in the returncircuit between said turbine and said pump, a ratchet mechanism to locksaid guide vane ring to said stationary casing when the pump and theturbine rotate at different speeds, the rigid convex dorsal portion andthe flexible concave ventral portion of each turbine blade constitutingtwo separate elements lying adjacent at their inlet ends.

3. In an hydraulic transmission, a stationary casing, a driving shaft, arotary pump secured to said driving shaft and provided with bladeshaving at least a flexible portion at their inlet ends, a driven shaftcoaxial with said driving shaft, a rotary turbine secured to said drivenshaft and provided with blades having a rigid convex dorsal portion anda flexible concave ventral portion, a guide vane ring in the returncircuit between said turbine and said pump, a ratchet mechanism to locksaid guide vane ring to said stationary casing when the pump and theturbine rotate at different speeds, the rigid convex dorsal portion andthe flexible concave ventral portion of leach turbine blade constitutingtwo separate elements lying adjacent at their inlet ends, whilst thepeculiar resiliency of the flexible concave ventral portion tends tomove its free end towards the rigid convex dorsal portion of theadjacent turbine blade.

4. In an hydraulic transmission a stationary casing, a driving shaft, arotary pump secured to said driving shaft and provided with bladeshaving at least a flexible portion at their inlet ends, a driven shaftcoaxial with said driving shaft, a rotary turbine secured to said drivenshaft and provided with'blades having a rigid convex dorsal portion anda flexible concave ventral portion, a

guide vane ring in the return circuit between said turbine and saidpump, a ratchet mechanism to lock said guide vane ring to saidstationary casing when the pump and the turbine rotate at differentspeeds, the rigid convex dorsal portion and the flexible concave ventralportion of each turbine blade constituting two separate elements lyingadjacent at their inlet ends, whilst the peculiar resiliency of theflexible concave ventral portion tends to move its free end towards therigid convex dorsal portion of the adjacent turbine blade, meansresponsive to centrifugal force in response to speed of the turbine forexerting on said flexible concave ventral elements of turbine blades astress having the same direction as that produced by the resiliency ofsaid elements.

5. In an hydraulic transmission, a stationary casing, a driving shaft, arotary pump secured to said driving shaft and provided with bladeshaving at least a flexible portion at their inlet ends, a driven shaftcoaxial with said driving shaft, a rotary turbine comprising a shellsecured to said driven shaft and provided with blades having a rigidconvex dorsal portion and a flexible concave ventral portion, a guidevane ring in the return circuit between said turbine and said pump, aratchet mechanism to lock said guide vane ring to said stationary casingwhen the pump and the turbine rotate at different speeds, the rigidconvex dorsal portion and the flexible concave ventral portion of eachturbine blade constituting two separate elements lying adjacent at theirinlet ends, whilst the peculiar resiliency of the flexible concaveventral portion tends to move its free end towards the rigid convexdorsal portion of the adjacent turbine blade, a ring mounted on theshell of said turbine to be angularly movable relatively to said shell,two semi-circular members responsive to centrifugal force in response tothe speed of the turbine, pivoted at one of their ends on said shell,means to connect operatively the other end of said members to saidmovable ring, fingers secured to said movable ring and arranged to bearagainst the convex face of the flexible ventral portions of the turbineblades.

6. In an hydraulic transmission a stationary casing, a driving shaft, arotary pump secured to said driving shaft and provided on the outletside with vanes substantially arranged in diametral planes and on theinlet side with pivoted flexible blades cooperating with the vanes, adriven shaft coaxial with said driving shaft, a rotary turbinecomprising a shell secured to said driven shaft and provided with bladeshaving a rigid convex dorsal portion and a flexible concave ventralportion, a guide vane ring in the return circuit between said turbineand said pump, a ratchet mechanism to lock said guide vane ring to saidstationary casing when the pump and the turbine rotate at differentspeeds, the rigid convex dorsal portion and the flexible concave ventralportion of each turbine blade constituting two separate elements lyingadjacent at their inlet ends, whilst the peculiar resiliency of theflexible concave ventral portion tends to move its free end towards therigid convex dorsal portion of the adjacent turbine blade, a ringmounted on the shell of said turbine to be angularly movable relativelyto said shell, two semi-circular members responsive to centrifugal forcein response to the speed of the turbine, pivoted at one of their ends onsaid shell, means to connect operatively the other end of said members,to said movable ring, ngers secured to said movable ring and arranged tobear against the convex face of the flexible ventral portions of theturbine blades.

'7. In an hydraulic transmission a stationary casing, a driving shaft, arotary pump secured to said driving shaft and provided, on the outletside with vanes substantially arranged in diametral plane but havingflexible outlet ends, and on the inlet side with pivoted flexible bladescooperating with the vanes, a driven shaft coaxial with said drivingshaft, a rotary turbine comprising a shell secured to said driven shaftand provided with blades having a rigid convex dorsal portion and aflexible concave ventral portion, a guide vane ring in the returncircuit between said turbine and said pump, a ratchet mechanism to locksaid guide vane ring to said stationary casing when the pump and theturbine rotate at different speeds, the rigid convex dorsal portion andthe flexible concavc ventral portion of each turbine blade constitutingtwo separate elements lying adjacent at their inlet ends, whilst thepeculiar resiliency of the flexible concave ventral portion tends tomove its free end towards the rigid convex dorsal portion of theadjacent turbine blade, a ring mounted on the shell of said turbine tobe angularly movable relatively to said shell, two semi-circular membersresponsive to centrifugal force in response to the speed of the turbine,pivoted at one of their ends on said shell means to connect operativelythe other end of said members to said movable ring, fingers secured tosaid movable ring and arranged to bear against the convex face of theflexible ventral portions of the turbine blades.

DIMITRI SENSAUD DE LAVAUD.

